WO2012155895A1 - Unité de transmission dotée d'un train épicycloïdal - Google Patents

Unité de transmission dotée d'un train épicycloïdal Download PDF

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Publication number
WO2012155895A1
WO2012155895A1 PCT/DE2012/100126 DE2012100126W WO2012155895A1 WO 2012155895 A1 WO2012155895 A1 WO 2012155895A1 DE 2012100126 W DE2012100126 W DE 2012100126W WO 2012155895 A1 WO2012155895 A1 WO 2012155895A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
rear wheel
wheel shaft
transmission unit
unit according
Prior art date
Application number
PCT/DE2012/100126
Other languages
German (de)
English (en)
Inventor
Karsten BETTIN
Original Assignee
Bettin Karsten
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bettin Karsten filed Critical Bettin Karsten
Priority to US14/118,248 priority Critical patent/US9180930B2/en
Priority to EP12724282.4A priority patent/EP2709898B1/fr
Priority to KR1020137031077A priority patent/KR101533586B1/ko
Priority to JP2014510660A priority patent/JP5748903B2/ja
Priority to CN201280023845.1A priority patent/CN103562058B/zh
Priority to DK12724282.4T priority patent/DK2709898T3/en
Publication of WO2012155895A1 publication Critical patent/WO2012155895A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62K—CYCLES; CYCLE FRAMES; CYCLE STEERING DEVICES; RIDER-OPERATED TERMINAL CONTROLS SPECIALLY ADAPTED FOR CYCLES; CYCLE AXLE SUSPENSIONS; CYCLE SIDE-CARS, FORECARS, OR THE LIKE
    • B62K25/00—Axle suspensions
    • B62K25/005—Axle suspensions characterised by the axle being supported at one end only
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/02—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of unchangeable ratio
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62K—CYCLES; CYCLE FRAMES; CYCLE STEERING DEVICES; RIDER-OPERATED TERMINAL CONTROLS SPECIALLY ADAPTED FOR CYCLES; CYCLE AXLE SUSPENSIONS; CYCLE SIDE-CARS, FORECARS, OR THE LIKE
    • B62K25/00—Axle suspensions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • B62M11/16—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears built in, or adjacent to, the ground-wheel hub
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only

Definitions

  • the invention relates to a transmission unit with planetary gear according to the preamble of claim 1, optionally for bicycles with small wheels or for trailer bicycles.
  • the largest spread to drive a bicycle has found the chain drive.
  • the drive sprocket connected to the pedal crank is axially seen mainly outside of the bicycle frame, while the mounted on the rear axle output sprocket axially seen mainly within the bicycle frame between the bicycle frame and rear wheel is arranged.
  • Multi-speed circuits for bicycles are preferably using chain drives
  • Bicycles with smaller wheels are preferably used to achieve small pack sizes and weights, often designed as folding wheels.
  • Bicycles with wheels of 14 inches and less require a translation between cadence and impeller frequency of at least 1: 5 in order to achieve a user-friendly deployment.
  • bicycles for bicycles for bicycles which are hung on the back of a bicycle and in contrast to the bicycles on which they hang, usually have much smaller wheels. So far, these wheels are usually gearboxes with similar translations used as for the bikes themselves. Thus, the person who rides on the trailer bike, drive at much higher cadence than the person on the bike to which hangs the trailer bike. Also, trailer wheels with small wheels require the above-mentioned translations between cadence and impeller frequency.
  • Solution a has the disadvantage that due to the different arrangement of drive sprocket (outside) and driven sprocket (inside) to the bicycle frame the
  • Bicycle frame between the sprockets must be passed through or over the chain drive away. Due to a variety of conditions (for example, the
  • Bicycle frame, bottom bracket and sprocket are as special components with appropriate
  • Solution c. has the following disadvantages:
  • the double chain drive requires a relatively large horizontal distance between bottom bracket axle and rear wheel axle.
  • the folding length of a folding bike is relatively large and the straight-line is unstable due to the less on the rear wheel driver weight.
  • these solutions require at least two gear stages (2 chain drives).
  • these solutions would then at least three gear stages (2 chain drives and a
  • Multi-speed hub in the rear wheel require.
  • the resulting high number of revolutions of the second chain drive requires a large amount of energy.
  • the torque is introduced from the crank to the bottom bracket.
  • the shaft-hub connection between the bottom bracket and the planet carrier of a downstream planetary gear must be large enough dimensioned because of not yet translated high crank forces and the relatively small diameter of the bottom bracket or as provided in DE 39 05 579 AI cohesively.
  • the gears to be used in the planetary gear on the crank must also be relatively large and therefore difficult to run. The resulting high number of revolutions of the chain drive requires a high expenditure of energy.
  • the planet carrier of the planetary gear and the output sprocket of the chain drive are axially seen on different sides of the bicycle frame.
  • the rear wheel shaft and any shaft-hub connections between output sprocket and rear wheel shaft or between the rear wheel shaft and planet carrier must be able to absorb high torque.
  • Planet carrier and rear wheel shaft must then either, as shown in DE 39 05 579 AI, are manufactured from one piece, whereby a very high material removal and cost of the rear wheel shaft would arise. Or between the rear wheel shaft and planet carrier a correspondingly large-sized shaft-hub connection must be provided. Overall, a considerable axial installation space between the chain line and reference center plane of the bicycle is required by the known variant.
  • Another disadvantage is that the force acting on the rear wheel shaft by the weight of the driver bending moment in the disclosed solution also on the
  • Planet carrier acts and affects the meshing of the planetary gear.
  • the arrangement of the planetary gear on the inside of the bicycle frame only one gear stage of the planetary gear can be realized because due to the arrangement of the
  • Torque transmission seen from the sun can be made only in the axial direction to the rear wheel.
  • Bicycle frame only one gear stage of the planetary gear can be realized, since due to the arrangement of the output sun gear as stored on the rear wheel sun gear, the torque transmission seen from the sun can be made only in the axial direction to the rear wheel.
  • the object of the invention is either for bicycles or for trailer bicycles one of the above solution e. also corresponding gear solution without the above-mentioned disadvantages of DE 39 05 579 AI or in DE 25 20 129 AI or in Fig. 20 to WO 2011/102606 A2 disclosed variants to develop, the transmission unit is to be suitable either for operating various types of the transmission unit upstream traction drives (chain drive and belt drive) or spur gears.
  • the sun gear does not need to be stored separately and thus radially seen within the sun gear switching means can be provided, which allow the execution of two juxtaposed sun gears and thus of two switchable gear ratios of the transmission unit.
  • Bicycle frame can be performed.
  • gear unit can be used in particular for bicycles with small wheel sizes of 6 to 16 inches and thereby very small center distances between bottom bracket and rear wheel shaft can be realized to achieve, for example, for folding bikes small folding dimensions.
  • the gear unit includes a one-way clutch, which is arranged between the sun gear or the sun gears and the rear wheel shaft, and thus neither within the impeller nor between the output gear of the transmission unit
  • an overrunning clutch must be provided, whereby different shapes of wheels used and can be firmly connected to the gear unit and whereby the same gear unit with the same achievable unfolding on different impeller sizes can be adjusted by simply with the driver at least in one direction of rotation rotatably connected output gear of Wegstoff- or spur gear is changed.
  • One-way clutch can be mounted and dismounted on the same side of the bicycle frame. G. that are achieved by the particularly space-saving with the features of the dependent claims transmission components ergonomically favorable Kettenlimenabnot that may be less than 40 mm.
  • Fig. 1 shows a preferred embodiment of the two-speed transmission unit with a switchable Stirnyak claw overrunning clutch and a one-armed suspension of
  • Gear unit in the bicycle frame which in combination with an upstream endless chain drive with triple sprocket, a six-speed transmission with uniform gear ratio can be realized.
  • Fig. 2 shows the circuit part of the two-speed gear unit with Stirniere claw overrunning clutch of Fig. 1, in which case the second gear is connected.
  • FIG. 3 and FIG. 4 are exploded views of the spur-dog jaw clutch of FIG. 1 in two preferred embodiments.
  • Fig. 5 shows the sectional view II through the first gear stage of the planetary gear of Fig. 1.
  • Fig. 6 shows the sectional view II-II through the second gear stage of the planetary gear of Fig. 1.
  • Fig. 7 shows the mountability of the overrunning clutch without removal requirement of essential parts the gear unit
  • Fig. 8 shows a preferred second embodiment of the transmission unit as a single-speed gear unit with Stirnyak claw overrunning clutch and one-armed suspension of
  • FIG. 9 shows the partially sectioned view III-III of the one-way clutch from FIG. 8.
  • Fig. 10 shows the mountability of the one-way clutch of the transmission unit of Fig. 8 without
  • FIG. 11 shows a preferred third embodiment of the transmission unit as a particularly compact and easy to manufacture one-gear transmission unit with a one-piece rear wheel shaft, FIG. with varied rear wheel attachment and with varied mounting of the gear unit in the bicycle frame.
  • Fig. 12 shows the jaw clutch between the driver of the gear unit and the
  • Fig. 13 shows a possible profile from which the planet carrier can be made as an extruded profile.
  • Fig. 14 shows a possible profile from which the impeller can be made as an extruded profile
  • Fig. 15 shows a preferred fourth embodiment of the transmission unit as a two-speed transmission unit with a feather-type coupling member and two-armed suspension of the transmission unit in the bicycle frame.
  • Fig. 16 shows the sectional view IV - IV through the first gear stage and the switching means of the embodiment shown in Fig. 15.
  • Fig. 17 is a partially cutaway view of the switching devices shown in Fig. 15;
  • FIG 1 shows the two-speed gear unit with front teeth claw overrunning clutch and one-armed rear suspension in the sectional view.
  • Gear unit upstream spur gear is non-rotatably operatively connected to a driver 3 of the gear unit via a shaft-hub connection, wherein the output gear 2 is secured for example by a locking ring 4 on the impeller 3.
  • Output gear 2 driven impeller 3 consists of a drive part 3 a and is axially formed according to a particular feature of the invention to the bicycle frame out as a planetary carrier 3b of a planetary gear.
  • output gear 2 and planet carrier 3b seen axially outside the bicycle frame. This allows the installation and removal of the chain 1 or the change of the output gear 2 to achieve various translations of the gear unit, without the rear wheel must be removed at the same time. Likewise, this allows the use of wedge or toothed belt or the use of spur gears, without being separated for installation and removal of the belt of the bicycle frame separated got to. All embodiments of the transmission unit upstream chain drives, wedge or toothed belt or spur gears are in addition to the embodiment shown by the invention. In this case, only the output gear 2 and optionally the shaft-hub connection between the output gear 2 and the drive part 3 a of the
  • a cranked output gear 2 is used according to a special feature of the invention, whereby an axially very space-saving arrangement of the planetary gear is achieved.
  • the arrangement also allows, in particular for the mass production alternatively driven wheel, impeller and planet carrier are made of one piece, for example as a casting. This embodiment is also encompassed by the invention.
  • the planet carrier 3b carries at least one, preferably three planetary axes 5, on each of which a planetary gear 6 is mounted with two stages 6a and 6b, wherein the stage 6a has a smaller and the stage 6b has a larger diameter. Only the stage 6a meshes with the ring gear 7 of the planetary gear. The ring gear 7 is connected via a ring gear 8 fixed to the bicycle frame 9. The stage 6a of the planet gears 6 meshes with the sun gear 10, the stage 6b of the planetary gears meshes with the sun gear 11.
  • the sun gears 10 and 11 are arranged coaxially with a rear wheel shaft 12, which in this embodiment according to a particular feature of the invention is made in two parts, consisting of a first shaft part, hereinafter referred to as the drive shaft 13, and a coaxially connected to the first shaft part second shaft part, hereinafter referred to as Schuradflansch 14.
  • the input torque for the transmission unit is from the output gear 2 on the
  • the torque is transmitted to the drive shaft 13 with an axially displaceable and with the drive shaft 13 rotatably operatively connected coupling member 15.
  • the coupling member 15 evenly distributed around the circumference of the front teeth 15a are arranged, which can engage in corresponding recesses of the sun gears 10 and 11 respectively.
  • the spur teeth 15 a of the coupling member 15 are penetrated by a the rear wheel shaft 12 perpendicular to the axis thereof, in a corresponding recess of the Rear wheel shaft 12 arranged and guided in corresponding recesses of the coupling member 15 pressure plate 16 axially pressed into the recesses of the respective sun gear 10 and 11, in Fig. 1 in the sun gear 10th
  • the impeller 3 formed to the planetary carrier 3b is, according to a particular feature of the invention, via the bearing 17 on the drive shaft 13 and over the bearing 18 in the
  • Compression springs 23 and 24 their force on the pressure plate 16, so the spur teeth 15a of the coupling member 15 are pressed by the pressure plate 16 due to the greater force of the compression spring 24 in the recesses of the sun gear 10 for a particular feature of the invention.
  • the difference of the spring forces of the compression springs 23 and 24 corresponds approximately to the spring force of the compression spring 23.
  • the torque is transmitted in this case from the planet carrier 3b via the stage 6a of the planet gears 6, which are supported on the ring gear 7, the sun gear 10 and from the sun gear 10 via the coupling member 15 on the
  • the second gear is switched according to a further special feature of the invention according to the structure and mechanism described below:
  • a shift screw 29 - preferably with
  • the shift nut 30 is part of a chain with chain links 31, which is connected to a suitable Bowden cable, not shown here.
  • the switching nut 30 is guided in a needle bearing 32, which in turn is mounted in the fastening screw 19.
  • Chain links of the switching chain 31 are supported in a guide bushing 33, which is mounted in the fastening screw 19 with the aid of a bearing 34.
  • For mounting the shift nut 30 with the shift screw 29 have drive shaft 13 and pressure plate 16 coaxial with the drive shaft 13 each have a bore into which a screwdriver for holding the shift screw 29 can be inserted.
  • Guide bushing 33 can not rotate with the drive shaft 13, these are supported by the needle bearing 32 and the bearing 34 in the drive shaft 13.
  • the shift screw 29 takes the guide bush 27 with it.
  • the guide bush 27 presses the compression spring 24 together.
  • the control chain 31 is pulled out of the drive shaft 13 until the guide bush 27 and pressure spring 24 have reliably lost contact with the pressure plate 16. Since the compression spring 24 no longer exerts force on the pressure plate 16, the weaker compression spring 23 pushes the pressure plate 16 and thus the front teeth 15 a of the coupling member 15 in the recesses of the sun gear 11.
  • the spring travel of the compression spring 24 is limited to avoid load peaks by the guide bushings 27 and 28.
  • the compression spring 24 can only be compressed so far until the guide bushings 27 and 28 touch. At the same time, this also ensures that the switching chain 31 can only be pulled to the right to the extent that no lever forces can act on the switching nut 30.
  • the shift nut 30 are designed as a threaded sleeve, in which case the shift screw 29 is screwed to the threaded sleeve and with the
  • Threaded sleeve is screwed. This embodiment is also encompassed by the invention.
  • the drive shaft 13 and the rear wheel 14 are connected by a threaded connection, which transmits the torque from the drive shaft 13 to the rear wheel 14.
  • the rear wheel flange 14 is seen radially inside a double row bearing, preferably a double row angular contact ball bearing 35, according to a particular feature of the invention stored, which radially outwardly superimposed the ring gear carrier 8, which additionally has a bearing shell for this purpose according to another particular feature of the invention.
  • the ring gear 8 is connected to the bicycle frame 9.
  • the angular contact ball bearing 35 is axially fixed in the ring gear 8 by means of a locking ring 36.
  • a washer 37 as a shaft side
  • the Hinterradflansch 14 at the periphery of at least three, preferably four or five
  • Embodiment as Speichenradnabe 40 a with connecting elements 40 b and 40 c executed between the wheel hub 40 a and rear wheel 14, can be screwed.
  • the gear unit is sealed by the sealed bearings 17, 34, 35, the plug 41 and the sealing rings 42 and 43 against the environment.
  • the sealing ring 43 is between a sealing cap 44 which is clamped between the output gear 2 and planet carrier 3b, and a contact cap 45 having a rising slope and fixed to the
  • Ring wheel 8 is connected, guided.
  • the sealing ring 43 is pushed onto the abutment cap 45.
  • the sealing cap 44 is pressed against the sealing ring 43, so that it is pressed according to another particular feature of the invention in the direction of the rising slope of the contact cap 45 and thus low-viscosity lubricant low-friction and space-saving, dynamic seal of the rotatably mounted planet carrier 3b against the firmly connected to the bicycle frame 9
  • the gear unit is connected to the bicycle frame 9 with fastening screws 46.
  • the fastening screws 46 transmit the reaction torque of the ring gear 7 fixedly connected to the ring gear carrier 8 to the bicycle frame 9.
  • drive shaft 13 has a centering surface.
  • rear wheel flange 14 has a centering surface for the rear wheel 40.
  • Fig. 2 shows the circuit part of the two-speed transmission unit with front teeth claw overrunning clutch, in which case the front teeth 15a of the coupling member 15 engage in the recesses of the sun gear 11 and the second gear of the transmission unit switch.
  • FIGS. 3 and 4 the method of operation of the one-way clutch will be explained below using the example of the second gear stage, the description correspondingly also applying to the first gear stage:
  • FIG. 3 and 4 show exploded views of the sun gear 11, the coupling member 15 and the pressure plate 16 in two preferred embodiments.
  • the coupling member 15 distributed at both ends on the circumference
  • the spur teeth 15a each have a chamfer 15b on the side facing the direction of rotation.
  • the sun gear 11 has, according to a further particular feature of the invention axially continuous recesses I Ia, in which engage the front teeth 15a of the coupling member 15 to the torque of the
  • the axially continuous recesses I Ia of the sun gears 10 and 11 have two advantages:
  • the clutch can be seen axially within a particular feature of the invention within the sun gears 10 and 11 and between the rear wheel shaft and teeth of the sun gears 10 and 11 are placed, which on the one hand no additional over the width of the sun gears 10 and 11 going out axial installation space is required, on the other hand, no front teeth to be machined front teeth must be provided on the sun gear 10 and 11, respectively. Rather, the sun gears 10 and 11 can be made over a greater length and then cut to length.
  • the space required for the coupling member 15 is created within the sun gear 11 by a simple bore I Ib.
  • Clutch member 15 is pressed freewheeling case by the bevel 15b from the freewheeling case sun gear 11 and compresses the compression spring 23, while the compression spring 23 presses the pressure plate 16 and the coupling member 15 against the sun gear 11 and the spur-claw clutch then engages again, when the re-driven sun gear 11, the drive shaft 13 passes again.
  • the bevels 15b of the spur teeth 15a penetrate slightly deeper in the end faces of the coupling member 15 at the point indicated in Fig. 4 with 15c.
  • an involute toothing 15d is provided, which transmits the torque from the coupling member 15 to the drive shaft 13.
  • an involute toothing 15d of the module 0.8 with 16 teeth according to DIN 5480 is used for the transmission of the torque from the coupling member 15 to the drive shaft 13, whereby the number of teeth is divisible by four and the Tar Vietnamese malmesser slightly larger than 12 mm and the tip diameter is slightly smaller than 14 mm.
  • Spur toothing of the coupling member 15 is provided. Those with divisible by four
  • both the coupling member 15 and the sun gears 10 and 11 can be manufactured solely by machining processes. In particular, for a cost-effective small batch production no cast parts are required.
  • Fig. 3 shows the embodiment shown in Fig. 1 of the coupling member 15 with pressure plate 16th
  • FIG. 4 for a further particular feature of the invention, an even easier to produce coupling member 15 is shown, being used as a pressure piece here no plate, but a round, flattened on both sides of the push rod 16 and the recesses of the coupling member 15 for guiding the push rod sixteenth can be produced by a simple bore 15e according to another particular feature of the invention.
  • the sun gear 11 in Fig. 4 for another particular feature of the invention milled bevels 1 ld, which have the same helix angle as the chamfers 15b of the coupling member.
  • the coupling member 15 is pressed in the freewheeling case on these bevels 1 ld from the sun gear 11.
  • FIG. 5 illustrates the sectional view II through the first gear stage of the transmission unit, wherein the bicycle frame 9 and arranged from the sectional plane II behind the bicycle frame 9 arranged rear wheel 40 are not shown.
  • Fig. 6 illustrates the sectional view II-II through the second gear of the transmission unit, wherein the chain 1, the bicycle frame 9 and seen from the sectional plane II-II from behind the bicycle frame 9 arranged rear wheel 40 are not shown and the ring gear 8 through the sealing cap 44 is covered.
  • Embodiments for the rear wheel 14 are provided. These too
  • Embodiments are encompassed by the invention.
  • many forms of rear wheels 40 can be used, which are either bolted directly to the rear wheel flange 14 or, as shown in Fig. 1, via additional elements 40a, 40b of the rear wheel 40 can be connected to the rear wheel 14.
  • Fig. 8 describes the sectional view of another preferred embodiment of
  • Gear unit with a gear stage of the planetary gear For reasons of clarity, the parts of the gear unit described in FIG. 1 and represented in FIG. 8 with a corresponding function have been designated in FIG. 8 with a number increased by 100 compared to FIG. Unless otherwise described below, the description of the parts in Fig. 1 for the corresponding parts in Fig. 8 is to be transmitted.
  • the transmission is designed as an input gear and for the realization of several gear steps for the drive system of the bicycle on the driver 103 a plurality of output sprockets 102a, 102b and 102c are arranged.
  • the coupling member 115 of the one-way clutch has only on one side of a spur gearing 115a and otherwise has no recesses for guiding the pressure plate 116.
  • the pressure plate 116 is held by a disc 147 in its radial position.
  • the pressure mechanism for the coupling member 115 of the one-way clutch allows an arrangement of the compression spring 124 on the side facing the impeller 103 of the pressure plate
  • the bearing of the driver 103 is effected by two bearing 117 and 118 mounted on the drive shaft 113 in this case by means of a bushing 148.
  • the rear wheel 140 is designed so that it can be attached directly to the rear wheel flange 14.
  • the shaft-hub connection between drive shaft 113 and rear wheel flange 114 is designed as a splined connection 113a.
  • the transmission is designed as an input gear, the coupling member 115 must be performed only as an overrunning clutch and non-switchable.
  • a driven wheel in the embodiment of FIG. 1, a driven sprocket assembly 102 with a plurality of output sprockets 102a, 102b, 102c, ff is used.
  • these principles are for deraille known - can thus realize a six-speed chain transmission with a uniform gear pitch and a short chain line spacing for the bike.
  • Sealing cap 144 and ring gear 108 through a simple gap seal which is a cost-effective embodiment, especially for higher-viscosity lubricant.
  • the coupling member 115 of the overrunning clutch has the following particularly space-saving design according to a special feature of the invention:
  • the coupling member 115 has only one end face a spur gear 115a and the coupling member 115 has no recesses for receiving and guiding the pressure plate 116.
  • the pressure plate 116 can be made rectangular and without further recesses.
  • a disc 147 is arranged, which holds the pressure plate 116 radially in position.
  • Angular contact ball bearing 135 is on the other hand, as in Fig. 1, a rear wheel 114 and a
  • the compression spring 124 is arranged with the arrangement described below on the side facing the impeller 103 of the pressure plate 116.
  • Fig. 9 the following described elements of the overrunning clutch in the partially sectioned view IIIIII of Fig. 8 are shown.
  • Drive shaft 113 is supported, holding a washer 127 at a distance from the pressure plate 116.
  • the compression spring 124 is supported, which in turn exerts an axial force on a guide bush 128.
  • the guide bushing 128 has a continuous
  • the guide bushing 128 directs the pressure force of the compression spring 124 radially seen within the compression spring 124 and within the pressure sleeve 125 back to the axial other side of the pressure plate 116. About the bore of the guide bushing 128, the pressure plate 116 is finally pressed against the coupling member 115. As in the description of Fig.3 and
  • the coupling member 115 is in this embodiment in the freewheeling case by the chamfers of the spur teeth 115a of the coupling member 115 from the
  • the driver 103 shown in FIG. 8 is provided by means of two bearings 117 and 118,
  • the driver 103 is secured to a particular feature of the invention against axial displacement by a circlip 120 mounted between the two bearings 117 and 118 in a groove of the driver 103.
  • a locking ring of the impeller 103 may also have a arranged between the bearings 117 and 118 offset.
  • Embodiment is encompassed by the invention.
  • the screw 119 fixed together with a washer 149, mounted on the spacer 148 bearings 117 and 118 axially against another retaining ring 121 which is on the drive shaft 113 between the
  • Sun gear 111 and the bearing 118 is arranged.
  • the retaining ring 121 is on the
  • Drive shaft 113 is positioned so that between the planet carrier 103b and ring gear 108 axially seen always sufficient distance and the planet carrier 103b
  • the rear wheel 140 can be made to connect directly to the rear wheel flange 114. This again makes it clear that the rear wheel flange 114 can accommodate a multiplicity of different rear wheel shapes, in this embodiment a rear wheel 140
  • Fixing screws 139 is attached to the rear wheel flange 114 and the radially outside has a commercially available rear wheel rim, not shown here, on which in turn a likewise not shown commercial bicycle tire can be mounted. According to a particular feature of the invention thereby short chain line distances can be realized because the reference center plane of the rear wheel 140, depending on the design and design of the rear wheel 140 in the direction of the bicycle frame 109 can be moved. Train.
  • a spline connection 113a for example, the one shown in Fig. 8 Toothed shaft connection 7x8 according to DIN 5481 used.
  • Spline connection 113a allows the transmission of high torques with a small radial installation space, so that in this preferred embodiment, the particularly small double row angular contact ball bearing 3201BTNG or the double row deep groove ball bearing
  • Drive shaft 113 and rear wheel flange 114 are in this case via a screwed onto the drive shaft 113 lock nut 138th
  • Fig. 9 shows the partially sectioned view III-III of the one-way clutch of Fig. 8 with the
  • Pressure plate 116 disposed within the drive shaft 113 compression spring 124, the pressure sleeve 125 and the guide bush 128th
  • Fig. 11 shows a further preferred and particularly compact and simply designed one-speed embodiment of the transmission unit.
  • the aim of this embodiment is a more cost-effective production compared to the embodiments of FIGS. 1 and 8.
  • Drive shaft and rear wheel flange are made in one piece and are combined to the rear wheel shaft 212.
  • the design of the sun gear 211 allows smaller numbers of teeth and thus smaller Total translations.
  • the fixation of the rear wheel 240 and the transmission of the torque from the rear wheel shaft 212 to the rear wheel 240 is effected by a simple threaded sleeve 239 in the rear wheel 240, which is screwed onto the rear wheel shaft 212.
  • Impeller 203 and planet carrier 251 are made in two parts.
  • the driver 203 is formed to the output gear 203 c of a gear train upstream of the toothed belt drive.
  • drive shaft and rear wheel flange consist of one piece and are combined to form a rear wheel shaft 212.
  • the sun gear 211 is provided in this embodiment with an end face toothing 211a or with frontal jaws, in which the front teeth 215a of the coupling member 215 can engage. This has the advantage that a smaller number of teeth can be selected for the sun gear 211 and thus a smaller overall ratio for the
  • Gear unit can be achieved.
  • the front teeth 215a of the coupling member 215 from the Stirnyak- connection.
  • Rear wheel shaft 212 is a washer 237, which can also be designed as a locking ring, as a shaft-side abutment shoulder for the angular contact ball bearing 235.
  • a rear wheel 240 seen radially inside a threaded sleeve 239, with the help of a rear wheel 240 and rear wheel shaft 212 connecting thread on the rear wheel shaft Screwed 212 and presses the angular contact ball bearing 235 for the purpose of axial fixation of the angular contact ball bearing 235 on the rear wheel shaft 212 against the washer 237.
  • a suitable choice of fit is a fitting portion 239 a of the threaded sleeve 239 via a tight fit with the
  • Rear wheel shaft 212 creates space within the rear wheel shaft, so that the compressive force of compression spring 223, unlike the embodiment shown in FIG. 8, does not have to be redirected axially and compression spring 223 can be placed on the side of pressure plate 216 facing rear wheel 240.
  • the compression spring 223 is supported by a
  • the gear unit in the bicycle frame 209 has a radially and laterally fixedly connected to the ring gear 208 connecting flange 254 at its periphery bores, which are aligned with the holes of the bicycle frame 209 and through the bicycle frame 209 by means of screw connections 246 with the ring gear 208 is attached.
  • Planetary gear has in comparison to the embodiments of Fig. 1 and Fig. 8 the advantage that the outside of the bicycle frame 209 can run from the gear unit to the bottom bracket in a straight line parallel to the reference center plane of the bicycle.
  • the driver 203 is formed in this embodiment to the output gear 203c of the gear unit upstream toothed belt drive.
  • the driver 203 and the planet carrier 251 are made in two parts.
  • the shaft-hub connection between driver 203 and planet carrier 251 is realized in a space-saving manner by a dog clutch. Further details emerge from FIGS. 12, 13 and 14 described below.
  • Fig. 12 shows an embodiment of a rotationally fixed claw coupling between the
  • Impeller 203 and the planet carrier 251 in the exploded view are Impeller 203 and the planet carrier 251 in the exploded view.
  • the driven gear 203c of the gear unit upstream toothed belt drive trained impeller 203 and / or the planet carrier 251 can be inexpensively made of extruded aluminum profiles.
  • Fig. 13 shows a possible profile for the planet carrier 251
  • Fig. 14 shows a possible profile for the driver 203.
  • For receiving the planet gears 206 is within the for the
  • Planetary carrier 251 provided profile by machining processes to make room. For reasons of manufacturing accuracy provided for receiving the planetary axes recesses of the planet carrier 251 may also be produced by machining processes.
  • the jaws provided on the driver 203 can also be produced by machining processes from the extruded profile intended for the driver 203.
  • Width of the rear wheel divided by two: 34/2 17 mm
  • Width of the bicycle frame at the height of the rear wheel + 8 mm
  • Width of the rear tire divided by two: 40/2 20.0 mm
  • Width of the output sprocket divided by 2: 2/2 + 1.0 mm
  • Screw connection or cohesively (by soldering, gluing, welding or in one piece) are provided.
  • Bicycle frame (9, 109, 209) and ring gear (8, 108, 208) and ring gear (7, 107, 207) are also included in the invention.
  • Fig. 15 describes the sectional view of another preferred embodiment of
  • Gear unit with two gears For reasons of clarity, the parts of the gear unit described in FIG. 1, FIG. 8 or FIG. 11 and represented with corresponding function in FIG. 15 have been compared with FIG. 1 by 300 in FIG Compared to Fig. 8 denoted by 200 or with an increased by 100 compared to FIG. 11 digit. Unless otherwise described below, the description of the parts in FIG. 1, FIG. 8 and FIG. 11 for the corresponding parts in FIG. 15 is to be transmitted.
  • the coupling member 315 is rotatably mounted in a recess of the rear wheel shaft 312 by means of a bolt 355.
  • the sun gears 310 and 311 have axially continuous recesses into which the
  • Coupling member 315 can engage. Depending on the desired switching position, the
  • Coupling member 315 either in the recess of the sun gear 310 or in the
  • Rear wheel shaft 312 manufactures.
  • the coupling member 315 has a further bore for
  • Receiving another bolt 356 which rotatably connects the coupling member 315 with a fork-like pressure piece 316.
  • the fork-like pressure piece 316 is in turn rotatably connected to a guide bush 328 by means of a further bolt 357.
  • the guide bushing 328 is mounted in a guide tube 353 mounted inside the rear wheel shaft 312 and can move axially in both directions. If the guide bushing 328 and thus also the fork-like pressure piece 316 moves away from the planetary gear, it rotates
  • Guide bushing 328 and guide tube 353 seal the gear unit to the tag chain 331.
  • the round nut 329 has a groove 329a.
  • the shift screw 330 of the switching chain 331 presses the groove of
  • the rear wheel 312 has a bore 312 a, through which the bolt 356 can be inserted when the corresponding holes of the Coupling piece 315 and the
  • Pulled sun 310 engages the coupling piece 315 in the recess of the sun gear 310, as soon as the recess of the sun gear 310 coincides with the co-rotating in the rear wheel shaft 312 coupling member 315.
  • the torque is now from the
  • Rear wheel shaft 312 co-rotating coupling member 315 coincides.
  • the torque is now transmitted from the sun gear 311 via the coupling member 315 to the rear wheel shaft 312, while the sun gear 310 rotates freely on the rear wheel shaft 312.
  • the rear wheel shaft 312 For receiving the feather key 361, the rear wheel shaft 312 has a further recess in the region of the rear wheel 340.
  • the one-way clutches are axially fixed by means of a nut 339 and a lock nut 338 on the rear wheel shaft 312.
  • Other embodiments of a one-way clutch between rear wheel shaft 312 and rear wheel 340 are conceivable and encompassed by the invention.
  • a freely definable Overrunning clutch between two deep groove ball bearings, which are arranged in the rear hub, are provided.
  • a possible varied fixation of the rear wheel 340 and a varrator bearing of the gear unit is shown on both sides of the rear wheel 340.
  • On the rear wheel shaft 312 are on both sides of the rear wheel 340 bearings 335 and 362, preferably simple deep groove ball bearings, arranged by means of a fastening nut 339 and with a lock nut 338 and through the spacers 363 and 364 separated with the two
  • Ring gear carrier 308 acts on the side of the planetary gear as a hub-side bearing shell, on the opposite side of the rear wheel 340 takes an additional bearing shell 365 the bearing 362 on. Both cups are releasably connected to the bicycle frame or to the dropouts 366 and 367 of the bicycle frame. Due to the shaft side required fixed fits of the bearings 335 and 362, the simple installation and removal of the rear wheel 340 is made possible in that the ring gear carrier 308 and the bearing shell 365 are releasably connected to the dropouts 366 and 367 of the bicycle frame and the rear wheel 340 with the entire Gear unit is installed and removed.
  • the ring gear carrier 308 is flattened for releasable connection of the ring gear carrier 308 with the dropouts 366 of the bicycle frame and for the purpose of space-saving transmission of the torque acting on the ring gear 308 via the ring gear 307 on the lower side.
  • a pressure piece 354 is pressed by means of two screwed into the dropout 366 screws 346, so that the force acting on the ring gear 307 and the ring gear 308 torque is absorbed by the dropouts 366 and the bicycle frame.
  • the bearing shell 365 can be flattened and fixed accordingly.
  • Transmission unit in the bicycle frame can also for the previously shown in Fig. 1, Fig. 8 and Fig. 11 embodiments of the transmission unit with the there used
  • Embodiments in not shown, easily modifiable form of the invention are.
  • the embodiment shown in FIG. 15, like the embodiments shown in FIGS. 1, 8 and 11, can also be embodied as a variant fastened on one side in the bicycle frame. Such an embodiment is also included in the invention.
  • sealing cap 344 and ring gear carrier 308 a sealing ring 343 is arranged in this embodiment, according to a further special feature of the invention, which is pressed by the sealing cap 344 on the beveled bevel of the planet carrier 303b and thus in turn allows a particularly space-saving dynamic sealing.
  • FIG. 16 shows a sectional view through the first speed stage and the shifting devices of the embodiment shown in FIG. 15.
  • the fork-like pressure piece 316 is made according to another particular feature of the invention of a round rod.
  • Fig. 17 is a partial sectional view of the switching devices shown in Fig. 15.
  • Embodiments of the invention are, for example, in the execution of the shaft-hub connection between the sun gear and rear wheel shaft for the one-speed transmission unit as a feather key connection. This allows an easy to produce rear wheel shaft.
  • the rear wheel shaft and the sun gear for the one-speed transmission unit can be made in one piece, so that the rear wheel shaft also acts as a sun gear at the same time.
  • low ratios of the gear unit for example, to 1: 5 can be achieved.
  • the one-way clutch according to FIG. 15 can be arranged between rear wheel shaft and rear wheel hub.
  • Impeller (3, 103, 203, 303) are arranged, for example by means of a particular commercially available for BMX wheels pawl overrunning clutch or a commercially available for deraille pinion package.
  • the advantage of low-cost production is the disadvantage that the planet carrier (3b, 103b, 251, 303b) and the planetary gears (6, 106, 206, 306) rotate in the freewheeling case with the result of efficiency losses. All of these embodiments are encompassed by the invention.
  • the ratios described in more detail below can be realized. In this case, reference is made by way of example to the embodiment of the toothed wheels with the module 0.8 according to FIG. 8 and FIG. 11.
  • Zahrrad modules are also included in the invention.
  • exemplary and preferred combinations of sprockets, output sprockets and numbers of teeth of the planetary gears are shown for the embodiments described above, which are among the preferred embodiments for the gear unit as a six-speed transmission with even gear gradation and / or by appropriate choice of the output Toothed ring are particularly easy to adapt to several impeller sizes.
  • Table A Six-speed gearbox for 14-inch and 12-inch wheels
  • Table B Six-speed gearbox for 10-inch wheels
  • the input gear unit shown in Fig. 11 can be adapted to the wheel sizes of 7 to 16 inches so that the same use-appropriate deployment is achieved by simply using different output sprocket with a varied number of teeth:
  • Table C Identical input gear unit for impeller sizes from 7 inches to 16 inches
  • the sun gear may again have smaller numbers of teeth, with which the gear unit for the smallest wheel sizes can be used.
  • Table D Identical input gear unit for impeller sizes from 6 inches to 14 inches

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne une unité de transmission dotée d'un train épicycloïdal, destinée sélectivement à des vélos ou à des vélos suiveurs. Ladite unité de transmission est conçu pour l'entrainement de petites roues arrières et contient un train épicycloïdal comportant une roue creuse (7) reliée au cadre de vélo (9), un support planétaire (3b) pourvu de roues planétaires (6a, 6b) et une ou deux roues solaires (10, 11), un arbre de roue arrière (12) qui est coaxial auxdites roues solaires ou un arbre de roue arrière qui est pourvu de la roue solaire précitée, un dispositif d'entraînement accouplé audit support planétaire ou un dispositif d'entraînement (3) réalisé sous forme d'un support planétaire (3b). Elle est caractérisée en ce qu'un palier (35) permet de monter l'arbre de roue arrière (12) radialement à l'intérieur du cadre de vélo (9), à savoir axialement entre le logement de la roue arrière (40) et ledit train épicycloïdal, ce dernier étant situé sur le même côté dudit cadre de vélo et comportant en amont une transmission, s'agissant par exemple d'une transmission à chaîne (1, 2). Cette disposition permet de réaliser des transmissions à courroie situées en amont, de courtes distances entre la roue arrière et l'axe de pédalier ainsi que des suspensions de type mono-bras au sein du cadre de vélo. Ladite unité de transmission permet de mettre en œuvre un ou deux rapports de transmission.
PCT/DE2012/100126 2011-05-18 2012-05-06 Unité de transmission dotée d'un train épicycloïdal WO2012155895A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US14/118,248 US9180930B2 (en) 2011-05-18 2012-05-06 Transmission unit with a planetary gearing system
EP12724282.4A EP2709898B1 (fr) 2011-05-18 2012-05-06 Unité de transmission dotée d'un train épicycloïdal
KR1020137031077A KR101533586B1 (ko) 2011-05-18 2012-05-06 유성 기어링 시스템을 가진 트랜스미션 유닛
JP2014510660A JP5748903B2 (ja) 2011-05-18 2012-05-06 遊星歯車装置を有するトランスミッションユニット
CN201280023845.1A CN103562058B (zh) 2011-05-18 2012-05-06 带有行星齿轮变速器的变速单元
DK12724282.4T DK2709898T3 (en) 2011-05-18 2012-05-06 PLANET DRIVE TRANSMISSION UNIT

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011050447.8 2011-05-18
DE102011050447A DE102011050447B4 (de) 2011-05-18 2011-05-18 Getriebeeinheit mit einer oder mit zwei Gangstufen, wahlweise für Fahrräder oder für Anhängefahrräder

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WO2012155895A1 true WO2012155895A1 (fr) 2012-11-22

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Application Number Title Priority Date Filing Date
PCT/DE2012/100126 WO2012155895A1 (fr) 2011-05-18 2012-05-06 Unité de transmission dotée d'un train épicycloïdal

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Country Link
US (1) US9180930B2 (fr)
EP (1) EP2709898B1 (fr)
JP (1) JP5748903B2 (fr)
KR (1) KR101533586B1 (fr)
CN (1) CN103562058B (fr)
DE (1) DE102011050447B4 (fr)
DK (1) DK2709898T3 (fr)
WO (1) WO2012155895A1 (fr)

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DE102011055748A1 (de) 2011-10-17 2013-04-18 Karsten Bettin Kompaktes zusammenklappbares Fahrrad
JP5829173B2 (ja) * 2012-04-27 2015-12-09 Ntn株式会社 車輪用軸受装置の製造方法
JP6209508B2 (ja) * 2014-12-25 2017-10-04 株式会社シマノ 自転車用ドライブユニット
US9945447B2 (en) * 2015-01-26 2018-04-17 Borgwarner Inc. Gear drive and actuator arrangement
DE102015210931A1 (de) 2015-06-15 2016-12-15 Schaeffler Technologies AG & Co. KG Anordnung zur Lagerung eines Sonnenrads eines Planetenradgetriebes
CN108883810A (zh) 2015-08-28 2018-11-23 先进技术有限公司 用于从链轮至轮毂的扭矩传动的传动元件
WO2017039440A1 (fr) * 2015-08-28 2017-03-09 Advancing Technologies B.V. Transmission de bicyclette à installer entre un support de pignon de chaîne et un moyeu de roue d'une bicyclette, ainsi qu'essieu de roue arrière et roue arrière comportant une telle transmission
CN105711728A (zh) * 2016-05-03 2016-06-29 程大鹏 通用型多挡位自行车变速器
US10160513B2 (en) * 2016-11-15 2018-12-25 Thomas Andrew Payne Modular cycle transmission structured including torque modifying components and other accessories
JP6587290B2 (ja) * 2017-03-01 2019-10-09 本田技研工業株式会社 駆動軸の支持構造
CN110871872B (zh) * 2018-09-04 2024-07-09 宁波市江北明达工业设计有限公司 实现自行车无级变速的无级变速装置
NL2021891B1 (en) * 2018-10-26 2020-05-13 Advancing Tech B V Transmission system
CN211766095U (zh) * 2019-12-02 2020-10-27 李守进 一种变级变速传动自行车
DE102020204885A1 (de) * 2020-04-17 2021-10-21 Robert Bosch Gesellschaft mit beschränkter Haftung Bremskrafterzeuger für eine Bremsanlage, Betätigungseinrichtung für eine Bremsanlage

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EP3154849B1 (fr) * 2014-02-28 2021-08-25 Advancing Technologies B.V. Vélo

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DE102011050447B4 (de) 2013-02-07
JP2014517226A (ja) 2014-07-17
US20140284897A1 (en) 2014-09-25
US9180930B2 (en) 2015-11-10
CN103562058B (zh) 2016-10-26
EP2709898B1 (fr) 2016-03-30
JP5748903B2 (ja) 2015-07-15
KR20140001256A (ko) 2014-01-06
DE102011050447A1 (de) 2012-11-22
CN103562058A (zh) 2014-02-05
KR101533586B1 (ko) 2015-07-03
EP2709898A1 (fr) 2014-03-26
DK2709898T3 (en) 2016-07-25

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